JP3422330B2 - How to switch a double-seat valve without leakage and a sealed arrangement for implementing this method - Google Patents

Description

The invention implements a method for switching a double-seat valve without leakage according to the preamble of claim 1 and a method according to the preamble of dependent claim 4 or 12. For a sealed arrangement for

From EP0039319B1, a sealing arrangement is known which can approximately carry out a method of the kind mentioned at the outset, but this sealing arrangement ensures a leak-free switching, not a leak-free switching. In this known sealing arrangement, the first closing member, which is embodied as a sliding piston with radial sealing means, is sealed in the area of its end portion in the open position of the double-seat valve by a second closing member. It The second closing member has at its end facing the slide piston a recess with a substantially cylindrical peripheral wall. The recess is dimensioned to hold the end portion of the slide piston in a sealed manner during the opening movement and in the open position before the second closing member opens. In the closed position of the double-seat valve, the slide piston, together with its radial sealing means, is retained in the cylindrical valve seat. The cylindrical peripheral surface of the recess in the second closing member is then in line with the cylindrical valve seat, the radial sealing means being arranged at the end of the slide piston and the valve being removed from the cylindrical valve seat. During opening, the slide piston is brought into sealing contact with the cylindrical peripheral wall of the row of recesses before contacting the second closing member.

This known sealing arrangement has the preferred embodiment EP00.
It is shown in Figure 2 of 39319B1 with all structural details. An essential feature of this sealing arrangement is that the radial sealing means is always supported and protected by the cylindrical peripheral wall both in the closed position of the valve, during the opening movement and in the open position. During the opening of the double-seat valve, the radial sealing means engages the peripheral wall of the recess of the second closing member, so that even in the valve open position the radial sealing means and the peripheral wall of the recess in the second closing member. Engagement is maintained. In this case, the engagement is exclusively frictional. That is, a surface pressure is generated between the peripheral wall and the radial sealing means only by the repulsive force generated inside the radial sealing means due to the elastic deformation of the radial sealing means, and the fluid contacting the radial sealing means causes the fluid to contact the two sealing members. It prevents them from flowing under pressure into the leak gap between them.

GB668563 makes it possible for radial sealing means (herein the so-called O-ring) arranged on a slide-shaped closing member to enter into the closing member formed as a seat disk during the opening movement of the valve, It is known that the valve rests in its open position. From this relatively old publication, it is known to form a cylindrical valve seat area, which acts in the closed position of the valve, with a diameter equal to the cylindrical recess in the seat disc. This valve has no possible leakage gaps between the closing members and the sealing arrangement is used above all for the protection and support of the radial sealing means, but due to the deformation of the radial sealing means the seat disc and the peripheral wall The frictional engagement acting with the radial sealing means must be sized so that the fluid contacting these sealing means does not reach under pressure the area of the recess in the seat disc located behind the seal. I won't.

The known sealing arrangement described above has several disadvantages.
The first disadvantage is that the tightness of the contact between the respective radial sealing means and the cylindrical peripheral wall of the associated closing member is only due to the frictional engagement due to the limited possibility of elastic deformation of the radial sealing means. Results from the fact that it is based. Furthermore, EP0039
FIG. 2 shows a preferred embodiment of the known sealing arrangement according to 319B1.
It is clear from this that in the closing movement of the valve the mounting of the closing member, which is embodied as a seat disk, is carried out unguided, at least with respect to the adjoining relationship between the radial sealing means and the cylindrical valve seat. This means that the closing member, which is embodied as a seat disc, first rests on its associated valve seat surface together with its axial sealing means, while the sliding piston rests in the recess together with the radial sealing means. Is based. Contrary to the described intent of the preferred embodiment, the radial sealing means, if for some reason the cylindrical peripheral wall of the recess containing the radial sealing means and the cylindrical valve seat are not in a row. The means are subjected to excessive mechanical load as they enter the cylindrical valve seat in the subsequent closing movement, which impairs their service life.

Corrective measures in this regard would be provided by embedding radial sealing means, here also formed as so-called O-rings, as also shown in FIG. As can be seen from the representation in the figure, the O-ring is "loosely" arranged in the groove in the non-deformed mounting position. However, the disadvantage of this arrangement is that behind the seals there are closed gaps towards the groove bottom, which are very difficult to reach by automatic cleaning or not at all when the detergent is passed through the valve. is there. Due to the so-called "loose" O-ring arrangement in the closing member, the O-ring is still somewhat movable inside its sealing groove in its deformed mounting position, so that the closing member formed, for example, as a seat disc is eccentric. When mounted, it can be deflected to some extent the next time it enters the coaxially offset cylindrical valve seat, thus avoiding overload and avoiding shearing effects.

Another disadvantage of the preferred embodiment of the known sealing arrangement is that it does not switch without leakage. EP0039
As is very clearly shown in FIG. 2 of 319B1, after the axial sealing means arranged in the seat disc rests on the associated valve seat surface, the radial sealing means is attached in subsequent closing movements. When entering the cylindrical seat of the valve, a temporary gap is formed between the two sealing means, trapping the fluid that was in the valve before closing. After the radial sealing means is completely retained on the cylindrical valve seat in the closed position of the valve, the fluid surrounded by the sealing means of the two closing members flows into the leak gap and through communication with the valve surroundings as a so-called switching leak. May appear.

Other proposals have been made to provide the sliding arrangement of the double-seat valve with a sealing arrangement with radial sealing means, but these proposals make it possible to avoid any one of the disadvantages mentioned above. In this connection, according to DE3242947C2, a preferably cylindrical annular passage is arranged as a leakage gap between two valve bodies each having a conical shaped stop surface, and Comes with a seal that comes into contact with the inner wall surface of the cylindrical annular path,
Sealing arrangements are known in which this seal is simultaneously used to seal the conical valve seat of the valve body. According to a preferred embodiment of this known sealing arrangement, the seal against the inner wall surface of the cylindrical annular passage forms a leakage gap between the first valve body and the second valve body with respect to the valve space. It is arranged between the stop faces of the two valve bodies so as to remain in the area of the annular passage during the switching of the first valve body or to make a sealing passage through the annular passage until a sealing communication occurs.

In the last-mentioned sealing arrangement, the seal is entirely embedded by form and friction engagement,
Although the creation of a gap between the seal and the associated groove is certainly prevented, this sealing arrangement also does not switch without leakage, as is clear from Figure 2 of DE3242947C2. EP003931
Unlike the sealing arrangement according to 9, the DE3242947C2 seals the valve internal space against the leak gap at the valve open position by allowing the first valve body, which also has the sliding function, to make the end face facing the leak gap into the second gap. It is carried out by axially applying pressure to the seal of the valve body. The first valve body is, above all, a seat disc, which is sealed by an axially acting sealing means against the associated valve seat surface in the closed position of the double seat valve. Therefore, basically DE324294
The double-seat valve according to 7C2 and the sealing arrangement realized therein belong to a different kind than the object of the present application. In this known valve closed position, the sealing action between the seal of the first valve body and the associated valve seat surface is achieved by axially pressing the seal against the valve seat surface.
In the open position of the valve, the sealing action between the two valve bodies and the sealing action against the leak gap causes the seal arranged on the second valve body to move axially towards the end face of the first valve body facing the leak gap. Only achieved by pressing. The "axial coupling" of the seal in the first valve body is a form engagement, the surface pressure of which is different from the object of EP0039319B1 in which the friction force is solely based on the deformability of the seal, the two valve bodies. Based on the sizing of the driver which defines the relative motion of the.

The double seat valve according to the superordinate EP0039319B1 essentially has the following main features:

1. When the double seat valve is in the closed position, the seal in the seat disc and the seal in the slide piston act independently of each other.

2. The seat disc has a cylindrical recess in which the radial sealing means of the slide piston is fully entered in the valve open position.

3.In the open position of the double seat valve, with radial seal,
The second closure member, i.e. the cylindrical inner peripheral surface of the recess in the seat disc, cooperates. Further, the diameter of the outer peripheral surface of the slide piston has a functional relationship with the diameter of the inner peripheral surface of the recess in the seat disk. That is, the diameter of the cylindrical valve seat is equal to the diameter of the cylindrical inner peripheral surface of the recess so that in the opening movement and the open position of the double seat valve the slide piston can be switched in a sealed state almost leak-free and retained in the recess. It is formed.

4. Axial seals in the seat disc are arranged to surround the recess at spaced intervals.

The object of the present invention is to ensure a leak-free switching by means of radial sealing means on the slide-shaped closing member of the double-seat valve, and furthermore in a microbiologically satisfactory arrangement of the radial sealing means. It is to improve the service life.

The problem is solved as a method by using the features described in the characterizing part of claim 1. Preferred configurations of the proposed method are described in the dependent claims. A sealing arrangement for carrying out the proposed method is realized by the features set out in the characterizing part of dependent claim 4 or 12, preferred configurations of this sealing arrangement being set forth in other dependent claims. .

The essential advantage of the method according to the invention is, on the one hand, that in the closing movement of the double-seat valve the two sealing means are guided to rest on the associated valve seat surface and, on the other hand, unlike prior art sealing arrangements, In the opening movement of the valves, the radial sealing means are guided by their cylindrical valve seats and remain sealed. In the first method form, these sealing means are such that their end portions are in sufficient sealing engagement with the sealing means in the second closure member. In the opposite direction, i.e. in the closing movement, the sealing means are in sealing engagement with each other long enough, until the radial sealing means are also reliably guided into the associated cylindrical valve seat.

The second proposed method form increases the service life of the sealing means by avoiding frictional relative movements between the sealing means. The essence of this method form is that the sealing means provided on the second closing member are in sealing engagement with the end portion of the first closing member and sealingly surround this end portion. . For both the radial sealing means and the sealing means provided on the second closing member, there is always a combination of materials consisting of the sealing means and preferably a metallic valve seat surface.

From the principles of the invention described above, two further preferred process variants are derived. First, the sealing engagement between the sealing means can additionally be formed as a form-fitting engagement, as in known sealing arrangements, not only by frictional engagement. The advantage of form-engagement is that the force acting between the contact points of the sealing means is not determined solely by the permissible deformation of the radial sealing means, but also by the relative movement between the closing members which can be influenced through the valve drive. And this relative movement is limited by the stopper between the two closure members. This stopper is a desirable safety stop for form-fitting engagements and a necessary stopper for frictional engagement configurations.

Secondly, another preferred method variant achieves leak-free switching to a degree that is not achievable with known sealing arrangements. To succeed in this,
On the one hand, in the closing movement of the valve, the radial sealing means sealingly engages the cylindrical valve seat surface before the sealing means of the axial closing member rests on the associated valve seat surface; The mounting of the sealing means on its associated valve seat surface begins radially inward and progresses radially outwardly thereof until it reaches the final position of the sealing means on the valve seat surface. by. In this case, the fluid between the valve seat surface and the sealing means is continuously extruded from the valve seat surface area from the inner side to the radially outer side, and it is ensured that this extruded fluid is enclosed. It can be avoided.

In order to carry out the method according to the invention, in an advantageous embodiment of the sealing arrangement, the sealing means in the second closing member, which has an axial sealing surface in a manner known per se, further comprises a radial sealing surface. Moreover, it mainly cooperates with the end portion of the sealing surface of the radial sealing means.

Advantageously, the radial sealing means of the first closure member has a convexly curved sealing surface of low curvature. By doing so, the radial sealing means sealingly engages the sealing means of the second closure member while being sealingly guided within the cylindrical valve seat surface.

In the sealed arrangement for realizing the second method form,
A radial sealing surface of the sealing means on the second closure member cooperates with an end portion of the first closure member such that when the closure members engage one another, the end portion is hermetically enclosed by the radial sealing surface. It has become. The final position is then limited by a stopper, preferably made of metal, which acts between the two closure members. This sealing arrangement gives all sealing means provided an extra long service life. This is because the material combination consists of a sealing means and preferably a metal valve seat surface.

It should be noted here that the sealing means of the second closing member is
It is not necessarily the axial sealing means as long as it does not engage the end portion of the radial sealing means. This method can also be applied in principle to a sealing arrangement in which the second closing member is formed as a sliding piston with radial sealing means.

Conveniently, the two sealing means are each formed as an integral elastomeric seal and are respectively embedded in the grooves which widen towards the groove bottom by form and friction engagement. This embedding in the form of so-called capsules ensures that the seal is not pushed out of the groove by the pressure of the generated fluid, and that there is a gap behind the seal due to the microbiological consequences. Certainly avoided with problems. Further proposed in this connection is to dimension the radial seal of the closing member formed as a sliding piston as a large volume ring,
There is less stress during sealing operation, and as a result of such circumstances, radial seal wear is reduced and life is extended.

The radial seal has a seal portion that protrudes from the groove when installed. According to a preferred construction of the proposed sealing arrangement, this sealing part can be formed so as to overhang the groove edges on both sides, so that it can be respectively supported radially there by a sliding piston. Such a support is advantageous on the one hand in sealing engagement with the sealing means of the second closing member and on the other hand in introducing or leaving the radial seal on the cylindrical valve seat surface. This is because the overhanging seal area enlarges the interference area of the seal, which does not cause stability problems.

The radial sealing surface of the sealing means of the second closing member or of the seal is conically narrowed in the direction of the opening movement of the valve, so that in addition to frictional engagement between the sealing means an advantageous shape is obtained. Engagement is achieved. The radial sealing surface thus formed acts as a transmission ramp in the independently actuatable and active slide piston for the radial sealing means, so to speak.

The axial sealing surface of the seal arranged on the second closing member rises from the inner side to the outer side in the radial direction and in the direction opposite to the attached valve seat surface, and further comprises a radial sealing surface. Forming a common all-round seal edge together,
This sealing configuration allows leak-free switching to the extent not possible with prior art sealing arrangements.

The proposed sealing arrangement is particularly suitable for the double seat valve known from WO93 / 16306. The embodiment shown in FIG. 3 of this publication can have all the advantages of the sealing arrangement proposed in the present invention. This known embodiment of the double-seat valve has a second closing member, which is embodied as a seat disc, which has a bore which is coaxially oriented with the cylindrical valve seat surface and which has the same diameter, and This hole is characterized in that it is guided to the periphery of the double seat valve. With such a configuration, the double-seat valve can be arranged horizontally and the leak gap can be completely discharged without being left.

In horizontal arrangements of double-seat valves, the drainage of leakage gaps is easier than in equal-diameter arrangements, because the holes provided in the second closing member have a larger diameter than the cylindrical valve seat surface.

In a horizontal arrangement of double-seat valves, an alternative form of the sealing arrangement, where the minimum residual amount may temporarily remain in the leak gap until it is removed from the area between the two sealing means in the next opening stroke. The inner diameter of the hole in the second closing member is smaller than the inner diameter of the cylindrical valve seat surface by twice the radial distance a, and the radial distance is 0.
To 0.5 mm, preferably a = 0.2 mm. By this measure, the seal of the second closing member, when viewed in the opening direction of the double-seat valve, is supported by the reduction of the diameter of the holes due to the radial distance a. The holes act in particular in a sealing engagement with the seal.

A second sealing arrangement, which preferably realizes the first method form, is a substantially axial mutual contact replacement of the generally radially directed engagement of the sealing means in the sealing arrangement described above. is there. This configuration is characterized by low wear. Furthermore, this configuration is less sensitive to dimensional errors and has more room for deformation than the first sealed arrangement. The radial sealing means is located at the end of the terminal portion of the first closure member and is defined by a transitional radial sealing surface and an axial sealing surface. The axial sealing surface of the axial sealing means in the second closure member has an outer portion cooperating in radial direction with the axial valve seat surface and an inner portion with an axial sealing surface adjacent to the radial sealing surface. Collaborate. In a preferred arrangement, the radial sealing means has a wall on the side facing the cylindrical valve seat surface, which widens towards the axial sealing means, the end portion adjacent to the axial sealing means, on the one hand, in the axial direction. Gaps are avoided when coming into contact with the sealing means, while ensuring optimal sealing and rubbing action. The final position of the two closure members relative to each other is limited in a sealing engagement by means of a stopper provided between the closure members.

The integrally formed seal disposed on the second closing member is embedded by form engagement and friction engagement in a groove that widens toward the groove bottom. On the other hand, it has been found to be advantageous to place an integrally formed seal in the recess of the first closure member, as is found in the alternative of the sealed arrangement. At that time, the concave portion is formed by the outer wall surface provided on the first closing member and the end surface following the outer wall surface.
This arrangement at the end of the terminal part of the first closure member ensures a simple assembly of the seal.

The stability of the seal arranged in the recess is improved by the fact that the seal comprises an insert according to another embodiment. Furthermore, with this insert, it is achieved that the seal deforms only in the areas important for the sealing action. In another advantageous configuration of the sealed arrangement,
In order to easily attach the seal to the first closing member and securely fix it to the recess, on the other hand, the outer wall surface forming the recess has a groove, and the ring is inserted into this groove at the seal attachment position. The part of the ring, which projects from the groove, forms with the insert part a form-locking engagement which acts inside the wall.

The axial sealing surface of the sealing means provided on the second closing member,
Ascending from the inner side to the outer side when viewed in the radial direction, when the second closing member rests on the attached valve seat surface, the liquid in contact therewith is pushed outward in the radial direction, and so on. This facilitates leak-free switching.

In the case where the sealing means are only in sealing engagement with one another by form-fitting and frictional engagement is not sufficient to limit the relative movement of the two closing members to each other, in another arrangement of the sealing arrangement, for example closing members. Alternatively, a stop, preferably made of metal, is arranged in the area of the drive means.

The proposed method and its advantages can also be realized by a sealing arrangement in which the closure member and the associated sealing means are each integrally formed and the working area of the sealing means is of elastomeric nature.

In the following, the proposed method will be explained with reference to the figures of the drawing for three selected sealing arrangements as examples.

1 to 4 are central cross-sectional views of the closing member of the double-seat valve in the area of the first sealing arrangement for carrying out the first method variant. However, FIG. 1 shows the closed position of the double seat valve, FIG. 2 shows the so-called retreat position, FIG. 4 shows the open position, and FIG. 3 shows the end or start of the sealing engagement of the radial sealing means on the associated cylindrical valve seat surface. Represent

FIG. 2a is also an enlarged central cross-sectional view of the arrangement according to FIG. 2 in order to show the essential features of the engagement of the sealing means with each other and with the associated valve seat surface.

FIGS. 5 to 8 show the valve position shown in FIGS. 1 to 4 of the closing member of the double-seat valve in the area of another sealing arrangement for carrying out the first method variant (closed position of the double-seat valve, FIG. 3 is a central cross-sectional view at a reef position, an end or start of the reef position, and an open position).

9 to 12 are central cross-sectional views of the closing member of the double-seat valve in the area of the sealing arrangement for carrying out the second method variant, in the four valve positions mentioned above.

The first closing member 3 formed as a sliding piston with a radial sealing means 1 (in the configuration according to FIG. 1 an integral seal 1 ^* with a convexly curved sealing surface 1a of small curvature) In the closed position of the seat valve, it is sealed and held inside the cylindrical valve seat surface 5. The second closing member 4, which is formed as a seat disc, has a sealing means 2 which in FIG. 1 is also formed as an integral seal 2 ^* . The sealing means 2 has an axial sealing surface 2a resting on an associated axial valve seat surface 5a. On the other hand, the radial sealing surface 2b, which is conically tapered in the opening movement direction of the double-seat valve,
It is exposed toward the leak gap 6. The axial sealing surface 2a and the radial sealing surface 2b form a common circumferential sealing edge K in the area of the circumferential surface of the cylindrical valve seat surface 5.

2, 3 and 4 show the opening process of the double seat valve. In FIG. 2, the sliding piston 3 slides in the direction of the second closing member 4 so that the radial seal 1 ^* has an end portion E.
Sealingly engages seal 2 ^* . At this time, the radial seal 1 ^* is guided by the cylindrical valve seat surface 5 and remains sealed. The seal 2 ^* is still on the axial valve seat surface 5a with the axial sealing surface 2a attached.

According to FIG. 3, the axial closing surface 2a of the second closing member 4 is separated from the axial valve seat surface 5a by a partial stroke h. At this time, the mutual sealing engagement of the seals 1 ^* and 2 ^* continues to exist. As a result of the sealing surface 1a of the seal 1 ^* being convexly curved with a small curvature, the seal 1 ^* is just off the cylindrical valve seat surface 5 and if the opening movement proceeds further from this position the cylindrical valve seat The guidance and sealing of the seal 1 ^* by the face 5 disappears.

FIG. 4 shows the fully open position of the double seat valve during the entire stroke H. At this time, the end portion E of the radial seal 1 ^* is hermetically enclosed radially inside by the seal 2 ^* ,
Moreover, it remains enclosed for the entire duration of the open position.

FIG. 2a shows details of the mutual sealing engagement of the seals 1 ^* and 2 ^* . 2 in the area of the end portion E of the radial seal 1 ^*
The two seals 1 ^* and 2 ^* are deformed. The radial sealing surface 2b, which is exposed in FIG. 1, now takes the position indicated by 1a "and 2b" with the associated sealing surface 1a in the end area E. The radial seal 1 ^* has, in the area outside the end area E, the contour indicated by 1a "', where the seal 1 ^{* is.}
In this area, is in close contact with the inlet 5b of the cylindrical valve seat surface 5. Seal 1 in form and friction engagement with each other
^{The joint} between ^* and 2 ^* in the introduction portion 5b is represented by K.

The radial seal 1 ^* is embedded in the groove 3a by form and friction engagement. The groove 3a extends from the groove edge 3c rounded toward the cylindrical wall surface of the slide piston 3 toward the groove bottom 3b. Such embedding or encapsulation is also provided for the seal 2 ^* , with the associated groove 4a, groove bottom 4b and groove edge respectively.
Shown at 4c. By embedding the seals 1 ^* and 2 ^* in the grooves 3a or 4a as shown, it is possible to avoid creating a gap behind each seal and to prevent the seals from being pushed out of the sealing groove under the influence of fluid pressure. .

Further, as is clear from FIG. 2a, in the seal 1 ^*, the portion 1b protruding from the groove 3a is projected onto the groove edge portions 3c on both sides,
There, they are respectively supported by the slide pistons 3 in the radial direction. With this measure, radial seal 1 ^*
The area of action of expands on both sides in the axial direction.

Furthermore, as shown in Fig. 2a, the axial sealing surface 2a of the seal 2 ^*
Rises from the inside toward the outside when viewed in the radial direction and in the direction opposite to the attached axial valve seat surface 5a. With this configuration, the placement of the seal 2 ^* in the closing movement is such that the contact between the seal 2 ^* and the axial valve seat surface 5a is such that the seals 1 ^* and 2 ^* are in the form engagement and the friction engagement with each other. , Starting at the seam K facing the valve seat surface 5a and progressing radially from the inside to the outside until reaching the final position of the seal 2 ^* on the associated axial valve seat surface 5a.

Further, as shown in Figure 2a, the second closure member 4
Has a hole 4d that is coaxial with the cylindrical valve seat surface 5,
Its inner diameter D4 is smaller than the diameter D3 of the cylindrical valve seat surface 5 by twice the radial spacing a shown. The radial distance a is selected in the range of 0 to 0.5 mm, but it has been found that a = 0.2 mm is particularly preferable. By reducing the inner diameter of the hole 4d, the seal 2 ^* becomes the groove edge 4c.
Are preferably supported in the area of, especially in a sealing engagement with the radial seal 1 ^* . If the double-seat valves are arranged horizontally to achieve a satisfactory discharge of the leakage gap 6, the diameters should be equal (D3 = D4).

It is not shown that the radial seal 1 ^* passes by the side of the seal 2 ^* towards the leakage gap 6 beyond the required relative movement of the closing members 3, 4 in the open position on the full stroke H,
It is preferably reliably prevented by a stopper made of metal. This stopper is the relative of the closing members 3, 4 required to achieve the planned fully open position of the valve and which defines the sealing engagement by the sealing and frictional engagement of the seals 1 ^* , 2 ^*. It works only after moving.

It has already been pointed out that the closure members 3, 4 and the associated sealing means 1 or 2 may be integrally formed, respectively, and the working area of the sealing means 1, 2 may have an elastomeric character. Except for the constructional measures and requirements associated with embedding separate seals 1 ^* , 2 ^* in their respective grooves, such an integral construction offers a method advantage compared to the advantages of the hermetically sealed arrangement described above. There is. The geometry of the outwardly facing sealing means is largely unaffected by this integral construction.

5 to 8 show another sealing arrangement for implementing the proposed first method of the invention. The recess of the first closing member 3 formed by the outer wall surface 3e and the end surface 3f following the outer wall surface 3e.
At 3g there is an integral seal 1 ^* with an insert 1e. The seal 1 ^* has a radial sealing surface 1c cooperating with the cylindrical valve seat surface 5 and also an axial sealing surface 1d.
The two sealing surfaces 1c, 1d are transitioning to each other. The second closing member 4 is provided with an axial sealing means 2 and an integral seal 2 ^* having an axial sealing surface 2a, the outer part of the seal 2 ^* being viewed in the radial direction being the axial valve seat. Cooperating with surface 5a, the inner part cooperates with axial sealing surface 1d adjacent to radial sealing surface 1c.

The procedure of movement from the closed position (FIG. 5) to the open position (FIG. 8) is in turn apparent from the individual figures. The description regarding the exercise procedure performed with respect to FIGS. 1 to 4 can be applied correspondingly to FIGS.

It can be seen that at the reef position (FIG. 6), the first closing member 3 is in contact with the stopper 4e provided on the second closing member 4. As shown here, if the outer wall surface 3e is formed in a substantially cylindrical shape so that the seal 1 ^* can be simply assembled,
The recess 3g cannot secure the shape engagement of the seal 1 ^{* by} itself. In order to achieve an effective form engagement, the proposed arrangement is such that the groove 1f is arranged in the outer wall surface 3e and the ring 7 is arranged in this groove 1f at the mounting position of the seal 1 ^*. There is. The part of the ring 7 protruding from the groove 1f forms, with the insert member, a form-locking engagement that acts inside the wall surface 3e. When assembling, combine ring 7 with seal 1 ^* surrounding it and stretch it,
It must be slid over the outer wall surface 3e and fitted into it in the area of the groove 1f. However, it is impossible to remove the seal 1 ^* without destroying it.

The sealing arrangement according to FIGS. 9 to 12 comprises two sealing means 1,
1 to 4 in that 1 ^* and 2,2 ^* do not directly engage each other
Essentially different from the sealed arrangement according to. Rather, when the closure members 3, 4 are engaged with each other, the radial sealing surface 2b of the axial sealing means 2 surrounds the end portion 3d of the first closure member 3. In the retreat position (FIG. 10) where the second closing member 4 having the axial sealing surface 2a of the axial sealing means 2 just leaves the attached axial valve seat surface 5a (FIG. 10), the first closing member 3 is The stopper 4e of the closing member 4 of FIG. The subsequent movement procedure from the reef position (Fig. 10) to the fully open position (Fig. 12) is clear from the representation shown. This sealed arrangement is characterized by a particularly long service life. This is because relative movement of the sealing means 1, 2 with respect to each other is avoided while the closing members 3, 4 are engaged with each other.

Front Page Continuation (72) Inventor Schleiber, Jürgen Germany D-23909, Ratzeburg, Otto Galber Strasse 3 (72) Inventor Paulic, Marx Germany D-21514, Büchen, Andia Beek 6 ( 56) References JP-A-59-99179 (JP, A) JP-A-56-164282 (JP, A) JP-B-3-26295 (JP, B2) JP-B-60-20629 (JP, B1) Special table Hei 7-503521 (JP, A) British patent 668563 (GB, B) West German patent application publication 3835944 (DE, A1) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16K 1/00-1 / 54 F16K 3/22-3/36

Claims (18)

(57) [Claims] 1. A radial closing means is provided in a slide-shaped closing member, which is arranged in a row with a first slide-shaped closing member (3) and is movable relative thereto. A second closing member (4) which is arranged so that the two closing members (3, 4) allow the fluid to flow from the first valve body part to the second valve body part in the closed position of the valve. Limiting the leakage gap (6) communicating with the valve perimeter in both the closed position and the open position, the first closing member (3) together with the radial sealing means (1) together with the closing position. Is sealed and held inside a generally cylindrical valve seat surface (5), in the open position it is sealed against the second closing member (4), and in the opening movement before the second closing member (4) opens. A method for sealingly engaging this with a double-seat valve switching without leakage, the method comprising: The sealing means (1) is arranged such that it remains guided and sealed by the cylindrical valve seat surface (5) during the opening of the valve, the sealing being provided in the second closing member (4). The means (2) may be the end portion (E) of the radial sealing means (1) or the end portion (3) of the first closure member (3).
d) in sealing engagement, characterized in that the respective end portion (E) or (3d) is hermetically enclosed by the sealing means (2) in the subsequent opening movement and in the subsequent opening position. , How to switch the double seat valve without leakage. 2. The sealing engagement between the sealing means (1, 2) or between the sealing means (2) and the first closing member (3) is effected by form-engagement or frictional engagement, and this engagement. 2. Method according to claim 1, characterized in that is limited by stoppers which define relative movement of the closing members (3, 4) with respect to each other. 3. The mounting of the sealing means (2) on the valve seat surface (5a) attached to it starts on the inside in radial direction and from there on the valve seat surface (5a) towards the outside. Method according to claim 1 or 2, characterized in that it proceeds radially to the final position of the sealing means (2). 4. Closing members (3, 4) arranged in a row and movable relative to one another, the closing members being arranged such that in the closing position of the valve the fluid flows from the first valve housing part to the second one. As a slide piston having a radial sealing means (1) which restricts the leakage gap (6) which prevents the gas from flowing out to the valve box part and communicates with the valve periphery at both the closed position and the open position. A first closing member (3) formed and a first closing member (4) formed as a seat disc with axial sealing means (2), said slide piston (3) In a closed position are sealed and held inside a generally cylindrical valve seat surface (5), in an open position they are sealed to a second closing member (4) and in an opening movement a second closing member (4). ) A double seat valve sealingly engaging the valve before opening). A sealing arrangement for carrying out the method according to any one of claims 1 to 3, wherein the axial sealing means (2) cooperates with an axial valve seat surface (5a). And a radial sealing surface (2b) cooperating with the end portion (E) of the sealing surface (1a) of the radial sealing means (1) or the end portion (3d) of the first closing member (3). A radial sealing surface (2b) sealingly encloses the respective end portion (E) or (3d) when the closing members (3, 4) are engaged with each other. A sealing arrangement for carrying out the method in a double seat valve according to any one of the preceding paragraphs. 5. Sealing arrangement according to claim 4, characterized in that the radial sealing means (1) has a convexly curved sealing surface (1a) of small curvature. 6. The sealing means (1, 2) are each formed as an integral elastomeric seal (1 ^* or 2 ^* ) and extend toward the respective groove bottom (3b or 4b) (3a). Alternatively, the sealing arrangement according to claim 4 or 5, characterized in that it is respectively embedded in 4a) by form-fitting and friction-engaging, the seal (1 ^* ) being formed as a ring of high volume. Constitution. 7. The seal (1 ^* ) overhangs the groove edge (3c) on both sides at the part (1b) protruding from the groove (3a), where each is radially supported by a slide piston (3). The sealed arrangement according to claim 6, characterized in that 8. The radial sealing surface (2b) of the sealing means (2) or seal (2 ^* ) is conically tapered when viewed in the opening movement direction of the valve. To 7
The sealed arrangement configuration according to claim 1. 9. An axial sealing surface (2a) of the sealing means (2) or seal (2 ^* ) rises from the inside to the outside when viewed in the radial direction, and the radial sealing surface (2b). Sealing arrangement according to any one of claims 4 to 8, characterized in that they together form a common circumferential sealing edge (K). 10. A closure element (4) according to claim 4, wherein the second closure member (4) has a bore (4d) formed coaxially with the cylindrical valve seat surface (5) and of equal diameter. The sealed arrangement configuration according to any one of claims. 11. The second closing member (4) has a hole (4d) coaxially oriented with the cylindrical valve seat surface (5), the inner diameter D4 of which is equal to that of the cylindrical valve seat surface (5). It is smaller or larger than the inner diameter by twice the radial distance a, and 0 <a ≤ 0.5 m.
Sealed arrangement according to any one of claims 4 to 10, characterized in that m, preferably a = 0.2 mm. 12. Two units arranged in a row and movable relative to each other
Has one closing member (3, 4), which in the closed position of the valve prevents fluid from flowing out of the first valve housing part from the second valve housing part and of the closed and open positions. In both cases, the leakage gap (6) communicating with the valve periphery is limited,
Furthermore, a first closing member (3) formed as a sliding piston with radial sealing means (1) and a second closing member (4) formed as a seat disk with axial sealing means (2). ) And the slide piston (3) is hermetically held inside the nebulized valve seat surface (5) in the closed position and in the open position against the second closing member (4). A double seat valve, which is sealed and in opening movement sealingly engages the second closing member (4) before opening, for carrying out the method according to any one of claims 1 to 3. In a sealing arrangement, said radial sealing means (1) is arranged at the end of the terminating portion (3d) of the first closing member (3), and the radial sealing surface (1c) and the axial direction which transition with each other. Radial sealing, limited by the sealing surface (1d) (1c) cooperates with the cylindrical valve seat surface (5), and the axial sealing surface (2a) of the axial sealing means (2) has an axial valve seat surface (5a) on the outer side when viewed in the radial direction. Double seat according to any one of claims 1 to 3, characterized in that the inner part cooperates with the axial sealing surface (1d) adjacent to the radial sealing surface (1c). Sealing arrangement for carrying out the method in a valve. 13. The sealing means (1, 2) are each formed as an integral elastomeric seal (1 ^* or 2 ^* ), the seal (2 ^* ) expanding towards the groove bottom (4b). The seal (1 ^* ) is embedded in the groove (4a) by shape engagement and frictional engagement, and the seal (1 ^* ) includes an outer wall surface (3e) formed on the first closing member (3) and an end surface (3) following the outer wall surface (3e).
13. Sealing arrangement according to claim 12, characterized in that the first closing member (3) is surrounded by form-fitting and frictional engagement in a recess (3g) made by f) and. 14. The seal (1 ^* ) is an insert member (1e).
14. The hermetically sealed arrangement according to claim 13, comprising: 15. The outer wall surface (3e) has a groove (1e), and a ring (7) is arranged in this groove at the mounting position of the seal (1 ^* ), and this ring projects from the groove (1f). 15. Sealing arrangement according to claim 13 or 14, characterized in that the recessed portion together with the insert member (1e) forms a form-fitting engagement acting inside the wall surface (3e). 16. Sealing means (2) or seal (2 ^* )
Sealing arrangement according to any one of claims 12 to 15, characterized in that the axial sealing surface (2a) of said rises from the inside towards the outside when viewed in the radial direction. 17. The relative movement of the closing members (3, 4) relative to one another is limited by a stopper (4e) which is necessary for achieving the planned fully open position of the valve. , And sealing means (1, 2) or seal (1 ^* ,
2 ^* ) Actuated only when the relative movement of the closing members (3, 4) forming a sealing engagement by form and frictional engagement is exceeded.
The sealed arrangement according to paragraph. 18. The closing member (3, 4) and the associated sealing means (1 or 2) are integrally formed, and the operating range of the sealing means (1, 2) has an elastomeric property. 18. A hermetically sealed arrangement according to any one of claims 4 to 17, characterized.